Ratchet mechanism.



R. A. NORLING.

RATGHBT MECHANISM.

APPLICATION FILED APR.30,1910.

1,1 30,925. Patented Mar. 9, 1915 3 SHEETS-SHEET 1.

THE NORRIS PETERS CON PHnTo-LITHQ. wAsHlNGmN. D

R. A. NORLING.

RATGHET MECHANISM. APPLICATION IILEDVAPR. 30, 1010.

Patented Mar. 9, 1915.

3 SHEETSSHEET 2.

ficrelzfor THE NORRIS PETERS 60., PHOTO LITHO v \VASMJNG run R. A. NORLING.

BATGHET MECHANISM.

APPLICATION FILED APB..30,1910.

1,130,925. Patented Mar. 9, 1915.

3 SHEETS-SHEET 3.

' @yfim, fiwww Q Ow Kane,

tureswith that shown and view of one of thepavvls.

1 UNITED STATES P EN OFFICE.

REINHOLD A. NORLING, or AURORA, ILLINOIS, ASSIGN'OR TO AURORA AUTOMATIC MACHINERY COMPANY, or AURORA, ILLINOIS, A CORIOBATION or ILLINoIs.

v RATCHET MECHANISM.

1,130,925. Original application filed May 7,

To all whom it may concern. 1

Be it known that I, REINHOLD A. Non- LI G, a citizen of the United States, and a resident of the city of Aurora, county of and State of Illinois, have invented certain new and useful Improvements in Ratchet Mechanism; and I do hereby declare that the following is a full, clear, and exact description thereof, reference being hadto theaccompanying' drawings, and to the letters of reference marked thereon, which form a part of this specification.

This invention relates to improvements in ratchet mechanism and consists of the mat- Y ters hereinafter described, and .more particularly pointed out in the appended claims.

The improved ratchet mechanism is shown herein as applied to a drilling machine constructed and arrangedto drill holes located in close proximity to. a wall or object, in a corner formcdby twowalls or surfaces located at right angles with each other or between two walls or objects located closely adjacent to each other, as isoften required in structural iron work, engine building, ship building and the like. The said drilling machine as herein shown and described is substantially identical as to its main feadescribed in an application filed by me on May 7th,'l907, Serial Number 372,407, Pneumatic drills, of which the present application is a division.

In the accompanying drawings :Figure 1 is'a central vertical section of a drilling machine provided with my improved ratchet mechanism, said section beingtaken axially through the drill spindle. Fig. 2 is a longitudinal section, taken on line 2-2 of Fig. 1. Fig. 3 is a longitudinal section, taken on the indirect line 33 of Fig. 1. Fig. 4 is a detail section illustrating the pawl and ratchet mechanism for rotating the tool spindle. Fig. 5 is a view illustrating the two pawl bearing levers and pawls carried thereby and the ratchet teeth of the drill spindle. Fig. 6 is a side elevation of one of the pawl levers. Fig. 7 is a perspective Fig. 8 is a side elevation of the drill spindle separate from its coacting parts.

Specification of Letters Patent.

Patented Mar. 9, 191 5.

1907, Serial No. 372,407. Divided and this application filed April 30, 1910.

7 Serial No. 558,616.

As shown in said drawings, 12 designates an elongated hollow frame or casing in one endof which is mounted a drill-spindle 13 and to the opposite end of which is attached thefpower cylinder of-an engine or motor. Said casing constitutes the principal part of a crank-case for the motor, and also an 'inclosure and support for the bearings of the drill-spindle 18 and the mechanism by which the drill spindle is operated from the motor. At one end the drill spindle 13 is provided with a socket to' receive the shank of the drill, and extends through the' wall of the casing, turning in a bearing 14: in said wall. Atits oppositeend said spindle engages a bearing member 15 affixedto the adjacent wall of .the casing, as hereinafter described. Said spindle is also provided,

.within the casing or frame, with aseries I of elongated ratchet-teeth 16 arranged par allel with theaxis of the spindle'and constituting part of the mechanism for driving or rotating said spindle. y 7 The motor as herein shown has the form of a two cylinder pneumatic engine, and

embraces .two parallel power cylinders, 17

17, located side by side and formed inasingle casting 18 flange 19 by which itis bolted orotherwise secured to the adj acent end of the casing or having-at its inner end a frame 12, as-clearly shown in Fig.1., The i pistons 20, 20 of said motor are connected by piston rods 21-, 21 and connecting rods '22, 22 with the two cranks 23, 2 3 of the crank shaft 24, Which'latter is mounted at its endsin the side walls of the'frame 12. .Thecrank-shaft 2 1 engages at its ends anti friction roller bearings 26' I11 O11Ilted in'the The said'piston 29 which slide in the drawings side walls of the frame. rods having cross-heads cross-head guides 30 shown-in as of cylindric form. are formed on plates 31 which. constitute" ,theinner cylinder heads and are attached by bolts tothe flange 19 on, the inner end of the cylinder casting, said plates-31 and the -flange 19 constituting an end wall for the.

end of the casing ders. Said inner cylinder heads fre equipped with bushings 33' through'which the piston rods slide.

12 adjacent to the cylin Thecross-he'ad guides J 35, designate valve chambers,= formed in the cylinder casting and located at the opposite sides and between said cylinders. Located in said valve chambers 35, 35 are the bushings 35 35, through which are formed the various ports leading to the cylinders and the supply passage for the motive fluid, as will hereinafter appear. Said valve chambers are open at their inner ends and closed at their outer ends by the end walls'36 36 of the bushings 35 35*. Re ciprocating in said valve chambers are piston valves, each designated as a whole by 37. Each of said piston valves is provided with two reduced parts 38, 38'wl1ich form three longitudinally separated, cylindric enlargements, by means of which, during the reciprocation of each valve, communication is afforded alternately between the inlet port 39 of said valve chamber, and ports 40, 41 communicating with the valve chamber and the opposite ends of the cylinders, as shown most clearlyin Fig. 3.

42, 43 designate exhaust ports. opening into the atmosphere, one at each end of the valve chamber, and which are brought alternately into communication with the cylinder ports 40, 41 through reciprocation of the piston valves. Said valves 37 are reciprocated from eccentrics 44 on the main crank-shaft24 through the medium of eccentric rods 45 connected at their ends respectively with eccentric straps surrounding said eccentrics 44 and with the piston valves, (Fig. 3). The inlet ports 39 of the valve chambers communicate with'a centrally located supply passage 47 formed in the cylinder castingconnected at its outer end with a tube 48 which is connected with the cylinder-casting by means of a screw-threaded nipple, as shown in' Fig. 1 and through which the motive fluid is supplied to the motor cylinders;

A throttle valve is located within the tube 48 for controlling the flow of the motive agent therethrough. Said valve embraces a conical valve or plug 50 adapted to engage a seat 5lformed on an annular flange within saidtube. The valve member is held normally against its seat by a spring 52 surrounding the stem 53 of the valve member and interposed between the valve member and an inwardly facing shoulder of a nipple 55 which has screw-threaded engagement with the outer end of said tube. The said valve member is provided with an inward axial extension or stud 56, which engages at its inner end the outer end of a hollow plug 57 located within and having end- Wise sliding engagement with the tube 48. The valve member 50 is lifted from its seat 7 through the medium of a sleeve 58 surrounding and having rotative movement on the tube 48 and confined betweenthe inner end of the nipple 55 and an annular exterior shoulder on said tube. Said sleeve isprovided with an-inclinedslot 59 through which extends a screw-stud 60 which has screw threaded engagement with the hollow: plug 57 before referred to. The tube 48 and its surroundingsleeve constitute a handle which is grasped by one hand of the operator in using the tool.- Rotation of said sleeve in I one direction operates through the action of 1 said'inclined" slot on the stud 60 to slide the hollow plug 57 and throttle valve 50 out wardly andthereby open the valve. Said inclined slot 59 is provided at its outer end with a transverse end portion adapted to be engaged by the stud :to hold the'valve so closure in its open position. The valve and mitting motion from-the crank-shaft24 to the drill-spindle, said mechanism embraces.

two swinging levers 61, 62 disposed oneover or at the side of the other and arranged to turn or rotate about the axis of the drillspindle, and provided'eachwith a pawl 66' adapted to engage the ratchet teeth 16 on the drill-spindle and turn the latter, when the lever is swung or moved inone direction, and to pass over said-teeth when the lever is swung in a reverse or backward direction.

Said levers are arranged to swing or oscillate reversely insuchmanner that when one of the levers is swung in a direction to rotate. the drill spindle forwardly the other lever is swung or moved backwardly or retracted;

each lever being-moved or swung forwardly,

or in a direction to rotate the spindle while a the other lever is being restored to-its'starts ing point. The said reversely swinging levers are so connected with the'mechanism which operates the same that the retracted lever is reversed and engages thedrill 'spin dle in a manner to turn the same forwardly before the lever which is then completing: its forward swing is released from-the drill spindle, whereby the rotation of the drill is made continuous. The said pawl carrying levers may be pivotally supported or mounted in any suitable way in the machine-frame or casing, but, as shown in the ing drawings, outer or forward ends with hubs 67 having smooth cylindric apertures which fit over and have bearing on thetoothed part of the drill-spindle. I

The levers are swung or vibrated through the medium of a secondary crank-shaft 70, parallel with the main crank-shaft 24, and provided with two crank-pins 7 1., 72 corresponding with the cranks of the main crankshaft. The secondary crank-shaft is rota a accompany-.. they are provided at theirtively mounted at its ends in antifriction roller bearings 7 3, 74 mounted, one set in one side wall of the; frame, and the other set in the cap or closure 25. Thesaid secondary crank-shaft is rotated from the main crank-shaft through the-medium of inter meshing gear-wheels V 75 and 76' on the secondary and main crank-shafts, respectively, said gear-wheels being arranged to drive the secondary shaft at the same speed that the primary crank-shaft is driven. The said levers are provided at their inner or swinging ends with laterally separated arms 78 between which the crank-pins 71, 72 of the secondary crank-shaft operate. Said fork-arms 78 of the pawl bearing levers have smooth inner parallel bearing surfacesand the crank-pins 71, 72 of the secondary crankshaft are provided with bearing blocks 80, 80, (each made of two halves or parts to facilitate the fitting thereof over the crankpins) which have smooth side or lateral faces for engagement with the inner faces of the fork-arms of saidpawl-bearing levers. It is obvious that the enlargement of the crank-pins of the secondary crank-shaft will produce the same effect as the bearing blocks described, but, for convenience of manufacture and to increase durability, the separate bearing blocks are preferred.

The operation of the secondary crankshaft, acting through the pawl bearing levers and their pawls to continuously rotate the drill-spindle will be apparent from a consideration of the following, in connection with Fig. 5 of the drawings. It will be observed that the crank-pins 71 and 72.,of said secondary crank-shaft arelocated 180 degrees from each other and each crank-pin turns, in giving the power-stroketo its associated lever, in the arc farthest awayfrom the drill-spindle. It will be also observed that, by reason of the angularity of the bearing surfaces of the arms of each lever to a line passing through the axis of; oscillation of the levers and the ,aXis of the secondary crank-shaft, as indicated, at 87 in Fig. 5,

when the lever is at the extreme limit of its vibratory movement in eachdirectiomthe center of the crank-pin is not on a line at right angles to the line 87, such as is indicated by the dotted line 85 inoFig. 5, but its said center is on a line at right angles to the bearing faces ofthe lever, and passing through the axis of the crank-shaft, such'as is indicated at 86, in said Fig. 5.v In other words, the movement of the said crank-pin in giving the power-stroke to the lever, is measured by the angular distance between the line 86 and a line similarly drawn through the axis of the crank-shaft at right angles to the straight bearing faces of the other lever, and is greater than .180 degrees by an amount equal to twice the angular distance between. the lines 85 and 86. That is to say, in the power-stroke from the lower position of the lever to its upper position, the cranlcpin will swing not onlythrough 180 degrees, but through an additional angle equal to the angle between the two positions of the levers. As a consequence the crankpin of said secondary shaft has amovement through an arc of more than 180' degrees, Whemtluring the'power-stroke of tlielever, the said crank-pin carries said lever from theextreme limit of its backward stroke to- ?the extreme limit of its forward stroke. It

follows, also that thecrank-pin, acting on the lever which is making its forward stroke advances said lever to a point at which the bearing faces of the lever are perpendicular to a line passing through the axes of said crank-pin' and the crank-shaft, and this 7 pointis at an angular distance from the location of the crank-pin in the mid-position of the lever, equalto ninety degrees plus the angle between the lines and 86 on Fig. 5.

On the other hand, it will be observed that therefore moving forward during the sented by thean'gle between the lines 85 and 86. Said crank-pins are shown in dotted lines in Fig. 5 asoccupyingpositions on the dotted line 85, and in full lines as occupying positions on the full line 86. Thus it will be observed that during the time the crank-pin,

acting upon thepawl bearing lever 61 ,which is completing its advance or power-stroke,

is" passing 'from the position indicated by theline 85 to the line' 86, the said lever 61 continues to advance. Duringthe same time the crank-pin 71, which has just retracted the pawl'bearing lever 62, is passing from the position indicated by the line 85 to the position indicated by the line 86 and during this part of the rotation of the crank-pin 71, the said pawl bearing lever 62 begins its forward swing to rotate the drill-spindle.

It follows that the effective action of the crank-pins of the secondary crank-shaft upon: each of said pawl bearing levers is 180 degrees plus twice the angle between the lines 85 and 86. It'will therefore be seen that the action of the secondary crankshaft through said pawl bearing levers 78 and 79' in rotating the tool spindle is a con- ,tinuous; one, the speed of rotation of the spindle being, of course, somewhat reduced when the levers are near the oppositelimits of their vibrating movement. Inasmuch as fore, bemade of relatively large size and with ample bearing surfaces.

Inasmuch as the secondary crank-shaft rotates in the direction indicated by the arrow in Fig. .2 and each crank-pin thereof rotates, during itspower stroke, in the arc farthest away from the drill-spindle, it will be seen that the greatest force of the pawl bearing devices is exerted in mid-position as shown in Fig. 2, and the greatest power is required to turn the drill-spindle, as it is then moving at its maximum speed. The lever is, however, at this time exerting its greatest leverage because its associated crank-pin of the second secondary. crankshaft'is at the same time operatingon the part of the lever farthest from the spindle.

So far as the cooperation of the pawl hearing levers with the crankshaft 70 is concerned, said crank-shaft may be rotated from any suitable source of power.

I arrange the crank-pins of the main crank-shaft at such angular distances apart that said crank-shaft exerts its greatest power to reciprocate the pawl bearing levers at a time when most needed, or at a time when the advancingpawl bearing lever is in its mid-position, as shown in Fig. 2. It will be understood that a double acting engine having parallel cylinders and arranged with the crank-pins of the crank-shaft at.

right angles to each other gives substantially uniform power throughout the full rotation of the .cranksshaft and further that if the crank-pins be placed at 180 degrees apart, the power of the two pistons will be exerted simultaneously with the result, however,

that both crank-pins will be simultaneously on a dead center at the endof each stroke. In order to more eflectively transmit power from the two pistonsto the vibrating levers I arrange the crank-pins of the main crank shaft so that the pistons act on both of said crank-pins when the latter are in position requiring the greatest power to turn the same, to wit, when the crank-pins of the secondary crank-shaft are passing through that part of their circular path farthest from the axis of oscillation of the levers. As shown in the accompanying drawings, thecrank-pins of the main crank-shaft are placed. at approximately 135 degrees apart, as indicated in Figs. 2 and 3, and as aresult, when the pawl bearing lever, which is making its driving or power-stroke, is at mid-position, both of the crank-pins of the i seekft are is Pasties rec iv pin, is approaching its dead center. When, L

however, theparts are in the position shown in Fig. 2, and one of the vibratory levers is in the middle of its advance or power-stroke and the other is being retracted, one-ofcthe crank-pins of the 1 main crank-shaft will be approaching the point in its path at whichi the crank-shaft receives maximum power from its associatedpiston, while the othe crank-pin will have passed suchpoint.

It follows that the work of impelling each lever, during the power or driving stroke of the same, will be divided between, or participated in by, both pistons. That is to say, one of the crank-pins of the main crankshaftwill come into such position thatits associated piston will exert its maximum driving, power on: the crank-shaft @when one of the levers is approaching, and until it reaches, a point midway of its power stroke, and the other cranki pin will then come immediately into such position that its'associated piston will exert its maximum power on the-crank-shanlnto complete the power stroke of such lever. The construction described, therefore, has the advantage that thetwo pistons act conjointly and success sivelyto exert maximum turning power on the crankshaft-during the time that each lever is effecting its driving or power stroke. Moreover, the construction described, has the further advantage that one of the motorshaft crankpins will be in position for the action of its associated piston during theef-f fective part: of the stroke of said piston,

when the other crankpin is on its dead center.

The pawl 66 illustrated has at its freeend an edge 90 for engagement with the spaces between the ratchet'teeth of the drill-spindle, and :at its opposite end a rounded or:

hinge portion ,91,Zmade-integral with the body of the pawl. The two pawls. are made of a combined width approximately equal to the length of the ratchet-teeth; The said pawl bearing levers are provided with sockets which receive the rounded or hinge portions 91 0f the pawls. The pawlsi are spring-pressed toward the ratchet-teeth by means of a form of spring made as follows: Each spring comprises an incomplete or split ring 92 surrounding the ratchet-teeth of the drill-spindle, (Fig.4) The terminals 93 of said springs are bent outwardly from the ring-like body of the spring in parallel relation to each other and grip'between. them. fiat faced .lugs S t {on the ends of the. Peril-,- The Pressure started by said nrieg serves to'hold the pawls yieldingly in position to engage with the ratchet-teeth, while permitting the pawls to spring outwardly to ridebackwardly over the said teeth. As illustrated, said springs 92, 92 are located between the hubs of the two pawl bearing levers, in. contact with each otheiij The construction of the tool spindle and the manner of mounting the same in the frame or casingis as described in the above named application of which this is aidivi= sion. One wall of the casing or frame is provided with a bushing 100 which constitutes the bearing for the lower cylindric portion of the spindle. On the upper or inner end of the said drill-spindle is mounted a ring or collar, constituting the rotative member of a thrust bearing, the non-rotative member of which consists of an annular flange 103, formed on a. tubular bearing member 105, which is secured in the top wall of the casing in axial alinement with the drill-spindle by means of a locking ring 102 which has screw-threaded engagement with the surrounding casing wall and clamps the flange 103 against an upwardly facing shoulder on said wall. Antifriction balls 104 are interposed between the rotative ring 101 and the flange 103. The hubs of the levers 61 and 62 are confined between and held from movement endwise of the drill spindle by contact with the bushing 100, and the ring 101. The sleeve 105 is extended downwardly or inwardly to form an externally cylindric bearing member 106 which fits within a cylindric bearing recess formed in the upper end of the drill-spindle. The bearings for holding the spindle laterally in place thus comprise the exterior bushing 100 at its lower end and the interior extension 106 of the fixed sleeve 105 at its upper end. The upward end thrust of the tool-spindle is resisted by the thrust-bearing formed by the ring 101, the flange 103, and the balls 104k. The said tool spindle is held from downward endwise movement by an annular shoulder 107 thereon, which bears against the upper or inner end of the bushing 100.

The upper sleeve 105 is made hollow and iuteriorly screw-threaded to receive a feedscrew 108 by which the drill is fed to its work, in a familiar manner. The said feedscrew is provided atits inner end with an axial projection 109 that extends through an aperture in a transverse diaphragm or wall 110 that constitutes the stop for the drillshank, said extension 109 being adapted to engage the drill-shank in a manner to eject the same from the tool-holder."

While I have shown the ratchet-mechanism described herein inconnection with a certain kind of drilling machine, in which its use is particularly advantageous for the reason that its construction permits of the evident that a location of the drill-spindle .closely adj acent one end of the frame orcasing which carries said spindle and the levers and other operating mechanism for the splndle and thereby renders possible the drilling ofa hole in awall'or like part closely adj acent'to a wall located at right angles thereto, in a corner,

or in other analogous situation, such as often occurs in structional iron work, in engine building, ship building and thelike, it being hole may be drilled by the device described in a wall or like part, the

center of which is as near an adjacent part having two crank-pins located at 180 apart and severally engaging said levers, said parts being so arranged that each driving stroke of each lever is effected in the movement of the crank-pin engaged therewith through the part of its path remote from the spindle and through an angular distance of more than 180 and means affording driving connection between each of said levers and the spindle acting to effect driving engagement of the spindle with the lever at the end of each backward stroke of the lever and give turning movement to the spindle with the lever through an angular distance equal to that of the full stroke of the lever and to also effect the release of the spindle from the lever during each backward stroke of the lever, whereby the turning movement of the spindle through the action of one lever begins before the turning movement of the said spindle through the action of the other lever ceases and continuous motion is imparted to saidv spindle.

2. In combination, a rotative spindle, two reversely swinging, spindle-actuating levers mounted concentrically with said spindle,

said spindle and levers being provided with coacting pawls and ratchet teeth, and a crank-shaft arranged parallel with the spin dle and having two crank-pins locatedat 180 apart and severally engaging said levers, said parts being so arranged that the driving stroke of each lever takes place in the movement of the crank-pin engaged therewith through the part ofits path remote from the spindle and through an angular distance of more than 180, said ratchet teeth being spaced at angular distances apart equal to the total throw of the levers, so that each pawl will come into driving engagement with one of the ratchet teeth at the end of each bac'k'waid stroke of the lever as my invention I aflixmy sigi'natur in the and will-give turning movement to the s'piiipresence of two witnesses, this 28 day offdle throughout the full length of each driv- April, A. D. 1910. ing stroke of the lever, and the turning x Y 1 I moir'ernent of the spindle with one lever will REINHOLD NORLING" begin before its-turning movement With'the Witnesses 7 ether lever ceases; Y J. R'BRADSHAW,

In testimony, tfirit I cl-stifii' the far-a eing CLARK EAGELSTON.

ciie'i of this patent my be obtained for five cents each; by addressing the Commissioner of Patent Washington, 10:0. 

